Accordion, folding and cutting apparatus

ABSTRACT

Apparatus for forming accordion folds in a longitudinally traveling web of substantially uniform width and indefinite length including web cutting means disposed upstream or downstream of said folding apparatus.

atent 1 4] ACCORDION, FOLDING AND CUTTING APPARATUS [75] Inventor: JohnDe Ligt, Covington, Va.

[73] Assignee: Westvaco Corporation, New York,

22 Filed: Aug.31, 1971 21 Appl.No.:1715,4 87

[52} U.S. Cl..l 270/79, 270/83 [51 1m. (:1; B65h 45/20- [58] Field ofSearch 270/21, 3940, 270/79, 73

[56] References Cited UNITED STATES PATENTS 2,675,747 4/1954 Greiner eta1 ..270/73 1,832,556 11/1931 Jensen et a1, 270/79 3,032,337 5/1962Holman 270/79 1,242,262 10/1917 Straubel.-. 270/39 1,109,296 9/1914Lewis.. 270/73 2,246,336 6/1941 Wyrick Primary ExaminerRobert W. MichellAssistant Examiner A. J. Heinz Attorney-W. Allen Marcontell & Richard L.

[5 7] ABSTRACT Apparatus for forming accordion folds in a longitudinallytraveling web of substantially uniform width and indefinite lengthincluding web cutting means disposed upstream or downstream of saidfolding apparatus.

6 Claims, 13 Drawing Figures gmma 81974 3,784,188

sum 1 0F 5 INVENTOR. J OH N DE LI GT PATENTEDJM: 819M 3.784.188

SHEEY 2 0F 5 JOHN DELIGT PATENIED 81974 SHEEY 3 {IF 5 lxvzsmwa JOHN DELIGT Pmmznm 819174 8.784.188

SHEET [IF 5 JOHN DELIGT f PAIENTED 81974 3.784.188

sum 5 or 5 JOHN DELIGT ACCORDION, FOLDING AND CUTTING APPARATUSBACKGROUND OF THE INVENTION 1. Field of the Invention The presentinvention relates to the field of paper converting and comprisesapparatus for accordion folding and cutting of a continuous paper websupply.

2. Description of the Prior Art The continuous, mechanized, accordionfolding of a paper web of indefinite length has long been a valuabletechnique in the process of coverting large, roll quantities of paperinto smaller, more convenient units suitable for individual consumerhandling. Through the years, many devices to perform this function haveevolved as the demand for greater web speed has increased.

Among such prior art devices have been inventions of Meisel, US. Pat.No. 568,307, and Teall, US. Pat. No. 1,290,800. Both of theseinventions, like that of the present, utilize identical link chaincarriers on opposite sides of an oncoming web having a multiplicity ofprojections secured with uniform spacing around the periphery of eachchain set which operatively cooperate to displace the web first to oneside of a center plane and then to the other, forming a small radiuscrease at the position of direction reversal. However, both of saidearlier inventions require substantial dynamic mass as related to thefold length: an intolerable characteristic for high speed machinery.

Moreover, due to the large turning radius of such prior art machines,similarly large clearances from the pointof crease formation to othercooperating machinery such as web cutters are required. An undesirableincident of such large clearances is the long, uncontrolled paper tailfollowing a prefold web cut which must be caught and drawn into theaccordion fold machinery to a point of positive control,

The present invention discloses a continuous web, accordion foldingapparatus suitable for construction with small, light weight elementscommensurate with high speed operation.

Another object of the present invention is to provide accordion foldingapparatus requiring small operational clearance to decrease theproximity between a pre-creasing web cutter and the first point ofpositive control within the folding apparatus.

Other objects of the present invention include the disclosure of apost-creasing web cutting apparatus for severing a continuous web in thebight ofa crease after the formation of same.

SUMMARY OF THEYINVENTION The folding apparatus of the present inventioncomprises two identical pairs of link-chain circuits, each pair beingdisposed on opposite face sides of an oncoming web of paper or otherthin sheet material of indefinite length. Chain circuits respective toeach pair are disposed for running in parallel planes around respectivesprocket sets. Each chain in a pair has secured thereto the respectivelyopposite ends of several tucker and gripper bars extending between andacross the two chains of a pair. Said tucker and gripper bars arepositioned perpendicularly to the chain running plane and distributedalternately at uniform intervals around the circuit periphery.

Each gripper bar comprises two, channel shaped structural members, eachhaving one leg thereof secured to one of two longitudinally contiguouschain links. The bight openings of said channels are disposed in facingopposition and filled with a soft, compliant substance such aselastomer.

Each tucker bar comprises a structural T element having the crossmemberthereof secured to respective chain links and the T leg projectingperpendicularly therefrom.

Operationally, the two chain pairs are synchronized whereby the tuckerbar on one chain pair coincides with the gripper bar nip opening oftheother chain pair. As the two, longitudinally contiguous links retainingthe gripper bar are turned over a small diameter sprocket, theconsequent angular divergence between the gripper faces causes a nip toopen therebetween. Said nip opening receives the tucker bar leg as itrolls a projection of the web into meshing contact with the nip opening.Separation from the sprocket returns the two contiguous gripper barcarrier links to a straight line geometry thereby closing the gripperfaces on the web held therebetween.

Since the straight-run sections of chain circuit departing from themeshing sprockets are aligned for slight relative divergence, the tuckerleg is withdrawn from the gripper nip at very slight planarmisalignment. As soon, however, as the tucker leg is withdrawn from thegripper, the chain angle of divergence is increased greatly by turningaround an idler sprocket having a chain engagement profile such as toretain a straight line geometry between the two contiguous gripper barcarrier links. This geometry prevents the gripper from opening andprematurely releasing the crease.

This increased divergence angle rapidly advances the web crease to thedesired release position where at the chain circuit is directed aroundanother, small diameter, conventional profile, sprocket for the purposeof opening the gripper to release the web.

If the web is to be cut following folding, a reciprocating blade engagesthe web along the crease bight. Simultaneously, a set of chain driven,cylindrical rollers are positioned against the web on the side oppositefrom the blade edge for loaded rolling contact there along to'cut theweb.

As an alternative embodiment of the invention, an interleaved series ofshort sheets may be accordion folded into a rectangular dispensing stackby prefold cutting the webs of two, independent supply streams intosheet length increments, merging the two supply streams into one, doublelayer stream with the transverse edges of one stream indexed to coincidewith the midpoint between sheet edges of the other stream and orientingthe double layer stream with the present folding apparatus to grasp,within the nip of a single gripper, two, serially adjacent, transversesheet edges within the linking bight of a laterally adjacent sheetcrease.

BRIEF DESCRIPTION OF THE DRAWINGS Relative to the drawings wherein likereference characters designate like or corresponding parts throughoutthe several views;

FIG. 1 is a line schematic of the accordion folding apparatus of thepresent invention integrated with a postfold cutting apparatus;

FIG. 2 is a partial elevational view of the folding apparatus of FIG. 1as seen at out IIII;

FIG. 3 is a detail of the chain carried tucker and gripper elements ofthe folding apparatus;

FIG. 4 is a schematic illustrating the mechanics operative in placing atransversely creased portion of web within the open nip of a gripperelement;

FIG. 5 is a geometric detail of the cam element for turning the foldingapparatus chain direction without prematurely opening the grippers;

FIG. 6 is a plan detail of the rolling cutter apparatus for cutting aweb after the accordion fold is formed;

FIG. 7 is an isometric schematic showing the power transmission train tothe rolling cutter apparatus;

FIG. 8 is a plan view of an alternative scheme for selectivelyretracting the rolling cutters from the reciprocating blade table plane;

FIG. 9 is a sectional elevation of FIG. 8 as seen across cut IX-IX;

FIG. 10 is a second alternate to the rolling-cutter apparatus of theinvention;

FIG. 11 is an exaggerated schematic of folded product from the apparatusillustrated in FIG. 12;

FIG. 12 is a folding apparatus of the present invention integrated witha prefold-cutting apparatus for producing the interleaved sheet productof FIG. 1].

FIG. 13 is a schematic of an alternative blade shape and associate webcutting pattern available from the roller-cutter apparatus of thepresent invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT 1. OPERATION FLOW SEQUENCEStarting with the FIG. 1 schematic, a paper web W of indefinite lengthis shown as delivered to the accordion folding apparatus at a controlledrate by pulling rolls 20. Right and left roller chain circuits 3a and 3bfunctionally cooperate in the proximal region A to alternately engagethe web W at regularly spaced distances along the web length. Theengagement forms a straight crease or pinch line extendingperpendicularly transverse to the web length axiswith the b'ightopenings of successive creases facing in alternately oppositedirections, i.e. away from the chain supporting that particular crease.

Each crease is carried by its respective supportive chain to the lower,release proximity B where the web panel W, is substantially horizontaland will gravity drop to a flat position without wrinkling.

Although this disclosure of the preferred embodiment describes theendless carrier elements 3a and 3b as roller chains, it should beappreciated that numerous alternatives, generically characterized asendless traction means, may be equally suitable for particularapplications. Among such alternative may be included other types ofchain drives, belts, ropes or cables. Relative rotational timing betweenthe two circuits 3a and 3b is critical since rigid elements structurallysecured to each circuit must physically cooperate by meshing. However,it is entirely possible to design a belt carrier system in which theinherent slippage between the traction carriers and the associate shea s(sprockets) is not so great as to be within meshing tolerance from onemeshing half cycle to the next. Coincident therewith, each incident ofmeshing would physically correct any misalignment of relative indexoccurring within the preceding half cycle of operation.

To cut the infinite length web W into uniform lengths terminatingprecisely along a creasebight centerline, a post-fold cutting mechanism4 is disposed between the folding apparatus and product receiving hopper9. If provision for cutting web creases falling on either side of webflow centerline C is desired, cutting mechanism 4 may comprise two bladetables 41a and 41b and two roller-cutting units 42a and 42b. Blade table410 and roller unit 4211 functionally cooperate as a set to sever creaselines on the right side of centerline C whereas table 41b and rollerunit 42b cooperate for left side cuts, exclusively.

An alternative embodiment is illustrated by FIG. 12 where prefoldcutting is performed on two web sources 10 and 11 for the purposeofinterleaving one panel section ofa folded sheet between integralpanels of a second, folded sheet.

2. FOLDING MECHANISM Each chain circuit 3a and 3b in FIG. 1 comprises apair of roller chains 30 encompassing sprockets 31, 32, 33 and cam 34.There being two, parallel, chain running planes, R and L (FIG. 2),having rigid transverse structural ties (tucker 35 and gripper 36), ineach chain circuit 30 and 3b, a total four chain closures, L30a, R30a,L30b and R30b, are described herein. It should be understood, however,that the number of running planes, e.g. R and L, may be increased forthe purpose of folding wider paper. To do so, would increase the numberof chain closures by two for each running plane added.

Both chain circuits 3a and 3b being of identical construction, furtherdescription will be focused on circuit 3a.

Relative to FIGS. 2 and 3, it may be seen that each gripper bar 36comprises two, longitudinal structural channel elements 61 filled withelastomer 62. The interface between the two elastomer portions 62 isseparable to form respective gripper jaws 66. The two elements 61 ofeach gripper bar 36 are respectively carried by the two, relativelyarticulatable, contiguous, link pairs 630 and 63i forming link set 64.Tabs 65, integral with the links 63, may be used as attachment platformsfor the channels 61 to the links 63.

Tucker bar 35 is shown to be a unitary, extruded T or L elementcomprising cross-bar S1 and leg projection 52. Like the gripper 36,tucker bar 35 may be secured to link pair 53 by means of an attachmentplatform 55.

The number of tuckers 35 and grippers 36 allowed on each chain circuitis arbitrary above the permissible minimum of 2 tuckers and 2 grippers.For purposes of timing, coordination, etc., there should be a wholenumber ratio between the sum of grippers and tuckers and the length ofthe circuit in pitches.

The distance D between a gripper 36 and adjacent tuckers 35 on the samechain is related to, but not the same as, a panel length S. Therefore,the linear quantity of web W pushed by the rolls 20 between chaincircuits 3a and 3b in the interim between points of tuckergripperengagement is greater than the distance D as represented by the sag inFIG. 1 web sections W, and W2.

The opening and closing operations of grippers 36 are functions ofrelative geometry as the chains are drawn over the periphery ofsprockets 31 and 32. The distance P(FIGS. 3 and 5) between chain rollers37 is held constant by the interconnecting rigid links 63. Accordingly,the sprocket pitch P may be defined as a chord subtending an a degreearc on the pitch circle M of radius of N (FIG. 4). Gripper faces 66 areplaced at a distance K (FIG. 3) above the plane including the axes oftwo adjacent rollers 37 and disposed to abut, or nearly so, betweensprockets when the roller center beneath the gripper face 66 falls intoa plane common to the centers of those rollers adjacent both sides.Since the geometry of a link pair 63 between adjacent rollers 37 isrigid, when a gripper bar unit 36, having cooperative jaw elements ontwo adjacent link pairs 63i and 630 of a link set 64, is drawn over theperiphery of a sprocket, the jaws 66 are separated by a mean distancesubstantially equal to 2(K) (Sin a). As the chain departs from contac-twith a sprocket, the roller centers return to the straight linerelationship thereby closing the 'jaws 66.

Rotational timing of the chain circuits 3a and 3b is as shown by FIGS. 1and'4 whereby the tucker leg 52 of one chain circuit rolls between theopened jaws 66 of gripper 36 on the opposite chain circuit. Since themeshing of cooperative tuckers and grippers is from opposite sides ofthe web W, a portion thereof is pressed between the open gripper jaws 66as shown in FIG. 4. As the chain rolls off the sprocket 31b, jaws 66 arepulled together to close on tucker leg 52, clamping the webW'therebetween.

In order to withdraw the tucker leg 52 from the nip of jaws 66 withoutdisrupting or damaging the web therebetween, the chains course halfangle of departure p from sprockets 31a and 31b must be held to shallowmaximums. The exact angle may be analytically derived bythose ofordinary skill in the art but for purposes of example, half angle p maybe in the order of 5.

At this point in the operation, gripper 36 -has established a crease inthe web and leg 52 of tucker 35 has been withdrawn therefrom. Moreover,the crease held by chain circuit 3b is slightly to the left (FIG. 1) ofcenter plane C. The next succeeding crease will be held by chain circuit3a and will be drawn to the right of center plane C thereby establishingan accordion geometry bias. However, no reliably repetitive fall patternmay be acquired or positive control exercised if the web is released.Wrinkles and irregular stacking patterns will result if the web isreleased from the positions W or W,.

Therefore, the generally vertical disposition of the ac cordion must bereoriented to a generally horizontal disposition as represented by websections W and W To accomplish this result, the creased end of websection W held by chain circuit 3b must be advanced laterally (to theleft) from the center plane C at a greater rate than the circuit 3a heldcrease of the same section web prematurely as the gripper bar 36 passesthereover.

To avoid this result, cam 34 of the present invention are provided withnotches 38 which are rotationally timed to receive the center roller ofthe three roller groups supporting a gripper bar link set 64. Asrepresented by FIG. 5 the centers of the three link set 64 supportiverollers 37 are allowed to sustain a straight line reltionship at thepoint of chain tangency to the idler 34. The depth and profile of thenotch 38 may be determined analytically by those of ordinary skill inthe art from chain pitch P, chain roller radius r, the initial departureangle a and the final departure angle B. Since link pairs 63i and 630are precluded from relative angular displacement as the set 64 turnsabout idler 34,

10 jaws 66 are held tightly closed on the crease of web W.

The next critical design point of the present invention is the verticalplacement of release sprocket 32 below idler 34. The controllingcriterion is the length of a moderately tensioned web secton W so thatgripper bar 36 on chain circuit 3b will open as the gripper 36 on chaincircuit 3a moves into position to pull the 3b circuit crease frombetween jaws 66.

If only continuous and rapid accordion folding of web W is desired, theaforedescribed. apparatus will flawlessly deliver a rectangular columncontinuum of accordion folded web to a receiving station such as chuteor hopper 9.

However, if finite lengths of folded web, in whole number increments ofweb sections between creases, are desired, the aforedescribed foldingapparatus may have integrated therewith the post-fold cutting mechanism4.

3. POST-FOLD CUTTING MECHANISM The preferred embodiment of the postfoldcutter comprises two blade tables 41a and 41b disposed in the same planebelow release sprockets 32.

The two tables 41a and 41b function alternately with one, 41a of FIG. 1,penetrating the material flow column between web sections W and W fromthe left of center plane C and the other, 41b, penetratingbetween websections W and W, from the right of center plane C.

Both tables 41a and 41b are provided with knife edges 43a and 43b forpositionmentwithin the bight of a crease.

Rotating into position against the knife edges 43a and 43b but fromopposite sides of the web W, are respective roller mechanisms 42a and42b. As best illustrated by FIG. 6 relatively wide, flat tread wheels 44cut the web W by pressing same againstthe knife edge 32a with rollingcontact. Resiliently loaded backing bar 45 maintains a relativelyconstant contact pressure between wheels 44 and the web W to assurecomplete cutting across the full web width as the edge and treadsurfaces wear. The treads of wheels 44 should be flat, i.e. relativelylong surface elements of a regular cylinder, to provide broadaccommodation for the degree of functional misalignment as eventually,if not initially, occurs in high speed, cyclically reversing machinery.I

Rollers 44 are mounted on carrier links 47 of a sprocket driven rollerchain 46. Spacing between rollers 44 along the chain 46 may be asdesired, one factor of consideration being the length of allowablecutting interim within an operational cycle: a smaller separationdistance between rollers yields a shorter cutting time for a given chainspeed.'

It should be appreciated that a cutting operation performed by theaforedescribed apparatus of this invention is not only rapid due tosimultaneous cutting of several small increments across the web widthbut is also neat, there being no opportunity for shredding due to blademisalignment. The present invention allows only one cut line, thatallowed by the continuous line of knife edge 43a or 43b, regardless ofthe variance the edge line may follow from true (within the limits ofthe wheel 44 tread width). Therefore, a single, continuous cut line maybe achieved with the rapidity of multiple cutters.

Although any number of mechanisms may be devised for selectivelyengaging the knife edges 43 with rollers 44, the schematic shown inisometric by FIG. 7 is of a particularly successful example. Knifetables 41a and 41b are mounted on guide bars 70 and reciprocably drivenby four-bar crank mechanisms 71a and 71b. Since the web cuttingoperation is cyclical over an interrupted period, greatest flexibilityfor programing the cycle period is afforded by linking the input powerline shaft 72 with the lateral, power transfer shafts 75a and 75bcarrying lateral spur gears 73a and 7311 through electrically latched,single revolution clutches 74a and 74]) such as a type 6 as specified bythe Hilliard Corporation of Elmira, NY.

Condition sensory means such as a limit switch or photo sensory switch,not shown, for actuating either of clutches 73a or 73/; by the emissionof a suitable electrical signal, may be responsive to select portions ofthe folding mechanism or drive therfor such as the notched cam 34.

With each operational cycle of the blade tables 41a and 41b, so too, arepositioned roller-cutter units 42a and 42b by means of carriage 48,parallel swing arms 49 and eccentric 77 driven connecting rod 76.

With clutch 74a engaged, for example, power is transferred from shaft 72to shaft 75a via spur gear 73a.

Shaft 75a transfers power to the four-bar linkage 710 via chaintransmission 78a (thereby sliding blade table 410 between web panels Wand W (FIG. 1)). Simultaneously, chain transmission 79a draws power fromshaft 75a to rotate eccentric 77a for raising the rollercutter unit 420into operative engagement with knife edge 43a mounted on blade table410.

Roller chain 46 carrying cutting wheels 44 is driven continuously bydirect power take-off 80a from main input power shaft 72 thereby furtherminimizing the cutter delay time.

As of the aforedescribed point of operation, the cutting cycle for thecrease joined web panels W and W is only half complete although the webis completely severed. However, since the ratio between the power shaft72 gear is 2:1 for a complete cycle, the one revolution clutch 74a mustbe actuated a second time to withdraw blade table 41a from the web flowcolumn. This second actuation may be keyed to such an event as thecompletion of a dump cycle for hopper 9 to remove the material collectedtherein and severed from the web W by the rolling-cutter apparatus.

After the cutting plane between guide bars 70 has been cleared by theretraction of roller-cutter 42a and blade table 41a therefrom, thecircuit for actuating cutting apparatus 41b and 42b is prepared forcompletion by a second panel counting circuit. In this manner, webcreases on sequentially opposite sides of the material flow axis C arecut with a predetermined number of integrally connected panelstherebetween.

It should be understood that the scale and disposition of elements inFIG. 7 is distorted to further the ends of clarity and disclosure.Although the gear and sprocket ratios of the FIG. 7 mechanism arecritical, they are so for a very limited product range. These arematters within the competence of ordinarily skilled practitioners of theart and need no further elaboration.

It should be noted, however, that depending on associated machinegeometry and the nature of power available, the rolling-cuttermechanisms disclosed by FIGS. 8, 9 and 10 may be more suitable.

The FIG. 8 and 9 embodiment, for example provides an alternative tophysically displacing a driven sprocket under load as required the FIG.7 mechanism. In FIGS. 8 and 9 the rolling contact surfaces are frustumsof regular cones 81 carried on an expansible chain circuit 82 loadedtensionally by reciprocable load shoes 83a and 83b. Linking piston rods84 fitted through cylinder block 85 rigidly unitize shoes 83a and 83bwhereby fluid pressure resiliently biased against an annular collarpiston surface (not shown) within the cylinder block 85 engages therolling contact surface 81 with the knife edge 43a. When the cut iscomplete, fluid pressure bias on the piston collar is reversed toretract all chains and roller elements from the blade tablereciprocation plane.

The rolling cutter mechansim of FIG. 10 is highly simplified andrepresents the basic elements of an application where the mostconvenient power application is a single or double stroke lineardisplacement of a machine element from point Y to point Z. The elementsof FIG. 10 include the arcuate segment of a cylinder having a radius E.The cyclindrical surface 86 is rolled into contact with the knife edge430 by driving a rod or roller element 87 along arcuate slot 88 frompoint Y to point Z. As surface 86 rolls about the axis F, the axisposition translates to point F.

FIG. 13 further illustrates the design flexibility available to thepresent invention by allowing complex cutting patterns such as theundulating or scalloped edge of panel W without sacrifice of cuttingspeed or precision. Since the thread width of rollers 37 exceeds theamplitude of knife edge 43c undulations, the cut line for web W willfollow exactly that of the knife edge notwithstanding the fact thatseveral rollers 37, rapidly traversing short increments of the webwidth, serve as separate anvils over respective increments.

Many variations of the scalloped edge scheme of FIG. 13 may becomprehended within the teaching of the invention, such as Greek scrollor sawtooth, the primary criterion being that the web W is pressedagainst all transverse elements of the edge 43c by loaded, rolling,contact pressure.

4. PREFOLD CUTTING MECHANISM Due to the relatively short radialclearance required by the sweep of tucker 35 and gripper 36 devices ofthe present invention, it is also possible to integrate the presentaccordion folding apparatus with prefold cutting apparatus to deliver acontinuum of interleaved, single folded sheets as schematicallyrepresented by FIG. 11. Distinctive characteristics of the FIG. 11product include sheets 23, folded so as to open to the left of thecenter line, and sheets 24, folded so as to open to the right of thecenter line. The upper panels 23u of sheets 23 are disposed to overliethe lower panels 24L of sheets 24. Conversely, panels 24u overlie panels23L. An integral pair of panels, 23a and 23L for example, are joined byhe bight of a crease 23b.

Relating now to the FIG. 12 apparatus for producing the product of FIG.1 1, there are shown two web supply streams l3 and 14 pulled from reelsl and 11 by pulling rolls 15 and 16. Rotary knives 17 and 18 cut therespective webs into a continuum of sheets 23 and 24, respectively.

Subsequent to cutting, the two supply streams are merged into a singleplane of supply 21 by the converging nip 22 between belt conveyors 25and 26. Rotation of the knife 17 is timed for 180 angular phasedisplacement from the rotation of knife 18 so that upon emergence fromthe nip 22, the transversely cut edges of serially adjacent sheets 23from supply stream 13 align with the approximate midpoint betweentransverse edges of laterally adjacent sheets 24. From the nip 22, thesingle supply stream 21 is delivered to the pickup area A betweensprockets 31d and 31b where the junction between serially adjacent edgesof sheets 23 and the midpoint of sheets 24 is pressed into the nip ofgrippers 36.

' As the foregoing cycle is reversed and repeated, panels fromrespective webs are interleaved in the manner represented by FIG. 11.

Having disclosed a specific,.preferred embodiment, I claim as myinvention:

1. Thin sheet material folding and cutting apparatus comprising:

means for reverse folding an indefinite length web of thin sheetmaterial into a continuum of transverse crease connected panels ofuniform length, the bight of a first crease open to a first directionand the bight of a second, successive crease open to a second direction;

planar support means reciprocable in a plane substantially parallel withsaid creases, said planar sup port means having a cutting edge forengaging a longitudinal element of a first transverse crease bight alongthe full lengththereof;

a rolling pressure surface having a line of rolling contact for pressingsaid web against said cutting edge;

support structure for said rolling pressure surface, said supportstructure including guide means for confining said line of rollingcontact to a plane parallel with said cutting edge;

pressure surface drive means secured to said support structure fordriving said rolling pressure surface alongsaid line of rolling contact;and,

transmission means to coordinate the engagement of saidcutting edge withthe bight of said first transverse crease from said first direction, tomove said rolling pressure surface ans support structure therefor intorolling pressure surface engagement with a face of said web oppositefrom said cutting edge and to energize said drive means for transverseseverance of said web.

2. Thin sheet material folding and cutting apparatus as described byclaim 1 wherein said transmission means further comprises means tosequentially withdraw a first planar support means cutting edge and afirst rolling pressure surface from said web engagement position and toengage said web along the bight of a second transverse crease between asecond planar support means cutting edge and a second rolling pressuresurface having supportstructu re therefor.

3. Thin sheet material folding andcutting apparatus as described byclaim 1 wherein said pressure surface drive means comprises an endlesstensile element driven about a planar periphery, a portion of said planar periphery being parallel with said planar support means cuttingedge, said rolling pressure surface comprising a plurality of wheelelements secured to said tensile element forrotation about an axisdisposed substantially perpendicular to said cutting edge.

4. Apparatus for cutting, folding and interleaving sheets of thinmaterial comprising:

two web supply streams of thin sheet material having substantiallyuniform width and indefinite length; web cutting means in each supplystream for cutting said stream into panels of uniform length, said twosupply streams subsequently merging into a single stream comprising twoparallel planar rows of said panels, said two cutting means beingrelatively synchronized whereby severed transverse edges of panels inone of said parallel planar rows align substantially midway betweensevered transverse edges of panels in said other row;

said single stream continuously entering the proximity between a pair offirst sprocket means, each carrying one of a pair of endless chainassemblies operatively disposed around respective closed circuits, eachof said chain assemblies comprising a plurality of chain links, each ofsaid chain links having one of two distally opposite ends thereofpivotally joined at a pivot axis to one such end of respectivelyadjacent links; tucker means and gripper means alternately securedaround the periphery of each said chain assembly, each gripper meanscomprising gripping elements respectively secured to two adjacent chinlinks whereby two gripping elements cooperatively converge whentraversing linear portions of said closed chain circuit to grasp thesheet material and open when traversing arcuate portions of said closedchain circuit, tucker means on one of said chain assemblies meshing withan open nip of gripper means on the other chain'assembly and viceversain the proximity between said first sprocket means to press a portion ofsaid single stream into said open nip whereby a longitudinal half panelof one row is disposed between crease connected half panels of the otherrow and vice versa;- each of saidchain assemblies following firstmutually divergent paths from first sprocket means to with draw saidtucker means from closed nips of gripper means; and, turning guide meansrespective to each chain assembly for directing same about a turningaxis from said first divergent path to a second, different divergentpath terminated by second sprocket means, said turning guide meansincluding grip retaining means for supporting in a substantially commonplane, the pivot axes of at least three pivot joints of two adjacentchain links respectively sup porting two cooperating gripping elementswhile in arcuate traversal about said turning axis whereby said grippingelements remain closed throughout said traversal. V 5. Apparatus asdescribed by claim 4 wherein said gripping elements comprise a barelement secured to each of said two adjacent chain links.

6. Apparatus as described by claim 5 wherein each said turning guidemeans further comprising a rotatable element having a peripheral supportsurface for said rerelative to said turning axis than the distallyopposite joints ofsaid adjacent gripping element supporting links.

Patent No 297 M: 188 I Dated January 8, 1974 John DeLigt Inventor(s) Itis certified that error appears in the above-identified patent and thatsaid Letters Patent are hereby corrected as shown below:

, Column 1, linel8, following "been" insert -the--. Column 7,

line 45, "cutter" should be --cutting--. Column 8, line 68,

following "joined by" correct the spelling of -'-the--. Column 9, line52, following "surface correct the spelling of and Signed and sealedthis 25th day of June 197M.

(SEAL) Attest:

EDWARD M.FLETCHER,JB. C. MARSHALL DANN Attesting Officer Commissioner ofPatents USCOMM-DC 60376-P69 L FORM PO-1050 (10-69) V a us. eovznuusmwnm'rmc OFFICE: 1959 o-ase-su

1. Thin sheet material folding and cutting apparatus comprising: meansfor reverse folding an indefinite length web of thin sheet material intoa continuum of transverse crease connected panels of uniform length, thebight of a first crease open to a first direction and the bight of asecond, successive crease open to a second direction; planar supportmeans reciprocable in a plane substantially parallel with said creases,said planar support means having a cutting edge for engaging alongitudinal element of a first transverse crease bight along the fulllength thereof; a rolling pressure surface having a line of rollingcontact for pressing said web against said cutting edge; supportstructure for said rolling pressure surface, said support structureincluding guide means for confining said line of rolling contact to aplane parallel with said cutting edge; pressure surface drive meanssecured to said support structure for driving said rolling pressuresurface along said line of rolling contact; and, transmission means tocoordinate the engagement of said cutting edge with the bight of saidfirst transverse crease from said first direction, to move said rollingpressure surface ans support structure therefor into rolling pressuresurface engagement with a face of said web opposite from said cuttingedge and to energize said drive means for transverse severance of saidweb.
 2. Thin sheet material folding and cutting apparatus as describedby claim 1 wherein said transmission means further comprises means tosequentially withdraw a first planar support means cutting edge and afirst rolling pressure surface from said web engagement position and toengage said web along the bight of a second transverse between a secondplanar support means cutting edge and a second rolling pressure surfacehaving support structure therefor.
 3. Thin sheet material folding andcutting apparatus as described by claim 1 wherein said pressure surfacedrive means comprises an endless tensile element driven about a planarperiphery, a portion of said planar periphery being parallel with saidplanar support means cutting edge, said rolling pressure surfacecomprising a plurality of wheel elements secured to said tensile elementfor rotation about an axis disposed substantially perpendicular To saidcutting edge.
 4. Apparatus for cutting, folding and interleaving sheetsof thin material comprising: two web supply streams of thin sheetmaterial having substantially uniform width and indefinite length; webcutting means in each supply stream for cutting said stream into panelsof uniform length, said two supply streams subsequently merging into asingle stream comprising two parallel planar rows of said panels, saidtwo cutting means being relatively synchronized whereby severedtransverse edges of panels in one of said parallel planar rows alignsubstantially midway between severed transverse edges of panels in saidother row; said single stream continuously entering the proximitybetween a pair of first sprocket means, each carrying one of a pair ofendless chain assemblies operatively disposed around respective closedcircuits, each of said chain assemblies comprising a plurality of chainlinks, each of said chain links having one of two distally opposite endsthereof pivotally joined at a pivot axis to one such end of respectivelyadjacent links; tucker means and gripper means alternately securedaround the periphery of each said chain assembly, each gripper meanscomprising gripping elements respectively secured to two adjacent chinlinks whereby two gripping elements cooperatively converge whentraversing linear portions of said closed chain circuit to grasp thesheet material and open when traversing arcuate portions of said closedchain circuit, tucker means on one of said chain assemblies meshing withan open nip of gripper means on the other chain assembly and vice versain the proximity between said first sprocket means to press a portion ofsaid single stream into said open nip whereby a longitudinal half panelof one row is disposed between crease connected half panels of the otherrow and vice versa; each of said chain assemblies following firstmutually divergent paths from first sprocket means to withdraw saidtucker means from closed nips of gripper means; and, turning guide meansrespective to each chain assembly for directing same about a turningaxis from said first divergent path to a second, different divergentpath terminated by second sprocket means, said turning guide meansincluding grip retaining means for supporting in a substantially commonplane, the pivot axes of at least three pivot joints of two adjacentchain links respectively supporting two cooperating gripping elementswhile in arcuate traversal about said turning axis whereby said grippingelements remain closed throughout said traversal.
 5. Apparatus asdescribed by claim 4 wherein said gripping elements comprise a barelement secured to each of said two adjacent chain links.
 6. Apparatusas described by claim 5 wherein each said turning guide means furthercomprising a rotatable element having a peripheral support surface forsaid respective chain assembly, said support surface having a depressiontherein synchronized to cooperate with that chain link pivot jointcommon to said two adjacent gripping element supporting links toaccommodate a more proximate radial position of said common jointrelative to said turning axis than the distally opposite joints of saidadjacent gripping element supporting links.